EP3428468A1 - Rolling bearing, bearing unit for air turbine, and air turbine handpiece for dental use - Google Patents
Rolling bearing, bearing unit for air turbine, and air turbine handpiece for dental use Download PDFInfo
- Publication number
- EP3428468A1 EP3428468A1 EP17763275.9A EP17763275A EP3428468A1 EP 3428468 A1 EP3428468 A1 EP 3428468A1 EP 17763275 A EP17763275 A EP 17763275A EP 3428468 A1 EP3428468 A1 EP 3428468A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- compressed air
- seal member
- inner ring
- lip part
- rolling bearing
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 238000005096 rolling process Methods 0.000 title claims description 92
- 230000002093 peripheral effect Effects 0.000 claims abstract description 61
- 238000011144 upstream manufacturing Methods 0.000 claims abstract description 20
- 239000013013 elastic material Substances 0.000 claims abstract description 8
- 239000002184 metal Substances 0.000 claims abstract description 8
- 230000000694 effects Effects 0.000 description 9
- 238000003825 pressing Methods 0.000 description 7
- 238000011282 treatment Methods 0.000 description 7
- 230000005489 elastic deformation Effects 0.000 description 5
- 238000009423 ventilation Methods 0.000 description 5
- 239000000314 lubricant Substances 0.000 description 4
- 238000005461 lubrication Methods 0.000 description 4
- 238000005520 cutting process Methods 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- -1 acryl Chemical group 0.000 description 2
- 238000004140 cleaning Methods 0.000 description 2
- 230000007423 decrease Effects 0.000 description 2
- 230000002349 favourable effect Effects 0.000 description 2
- 238000004904 shortening Methods 0.000 description 2
- 230000001954 sterilising effect Effects 0.000 description 2
- 238000004659 sterilization and disinfection Methods 0.000 description 2
- 230000004913 activation Effects 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 230000004043 responsiveness Effects 0.000 description 1
- 230000035945 sensitivity Effects 0.000 description 1
- 239000007921 spray Substances 0.000 description 1
- 230000036346 tooth eruption Effects 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Images
Classifications
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- A—HUMAN NECESSITIES
- A61—MEDICAL OR VETERINARY SCIENCE; HYGIENE
- A61C—DENTISTRY; APPARATUS OR METHODS FOR ORAL OR DENTAL HYGIENE
- A61C1/00—Dental machines for boring or cutting ; General features of dental machines or apparatus, e.g. hand-piece design
- A61C1/08—Machine parts specially adapted for dentistry
- A61C1/12—Angle hand-pieces
-
- A—HUMAN NECESSITIES
- A61—MEDICAL OR VETERINARY SCIENCE; HYGIENE
- A61C—DENTISTRY; APPARATUS OR METHODS FOR ORAL OR DENTAL HYGIENE
- A61C1/00—Dental machines for boring or cutting ; General features of dental machines or apparatus, e.g. hand-piece design
- A61C1/02—Dental machines for boring or cutting ; General features of dental machines or apparatus, e.g. hand-piece design characterised by the drive of the dental tools
- A61C1/05—Dental machines for boring or cutting ; General features of dental machines or apparatus, e.g. hand-piece design characterised by the drive of the dental tools with turbine drive
-
- A—HUMAN NECESSITIES
- A61—MEDICAL OR VETERINARY SCIENCE; HYGIENE
- A61C—DENTISTRY; APPARATUS OR METHODS FOR ORAL OR DENTAL HYGIENE
- A61C1/00—Dental machines for boring or cutting ; General features of dental machines or apparatus, e.g. hand-piece design
- A61C1/08—Machine parts specially adapted for dentistry
- A61C1/10—Straight hand-pieces
-
- A—HUMAN NECESSITIES
- A61—MEDICAL OR VETERINARY SCIENCE; HYGIENE
- A61C—DENTISTRY; APPARATUS OR METHODS FOR ORAL OR DENTAL HYGIENE
- A61C1/00—Dental machines for boring or cutting ; General features of dental machines or apparatus, e.g. hand-piece design
- A61C1/08—Machine parts specially adapted for dentistry
- A61C1/18—Flexible shafts; Clutches or the like; Bearings or lubricating arrangements; Drives or transmissions
- A61C1/181—Bearings or lubricating arrangements, e.g. air-cushion bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03D—WIND MOTORS
- F03D80/00—Details, components or accessories not provided for in groups F03D1/00 - F03D17/00
- F03D80/70—Bearing or lubricating arrangements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
- F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
- F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or balls
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/72—Sealings
- F16C33/726—Sealings with means to vent the interior of the bearing
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/72—Sealings
- F16C33/76—Sealings of ball or roller bearings
- F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/72—Sealings
- F16C33/76—Sealings of ball or roller bearings
- F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
- F16C33/7816—Details of the sealing or parts thereof, e.g. geometry, material
- F16C33/782—Details of the sealing or parts thereof, e.g. geometry, material of the sealing region
- F16C33/7823—Details of the sealing or parts thereof, e.g. geometry, material of the sealing region of sealing lips
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C41/00—Other accessories, e.g. devices integrated in the bearing not relating to the bearing function as such
- F16C41/001—Integrated brakes or clutches for stopping or coupling the relatively movable parts
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/16—Sealings between relatively-moving surfaces
- F16J15/164—Sealings between relatively-moving surfaces the sealing action depending on movements; pressure difference, temperature or presence of leaking fluid
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/16—Sealings between relatively-moving surfaces
- F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
- F16J15/3204—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2240/00—Components
- F05D2240/50—Bearings
- F05D2240/54—Radial bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2240/00—Components
- F05D2240/55—Seals
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2316/00—Apparatus in health or amusement
- F16C2316/10—Apparatus in health or amusement in medical appliances, e.g. in diagnosis, dentistry, instruments, prostheses, medical imaging appliances
- F16C2316/13—Dental machines
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2360/00—Engines or pumps
- F16C2360/31—Wind motors
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E10/00—Energy generation through renewable energy sources
- Y02E10/70—Wind energy
- Y02E10/72—Wind turbines with rotation axis in wind direction
Definitions
- the present invention relates to a rolling bearing, a bearing unit for an air turbine, and an air turbine handpiece for dental use.
- a small and lightweight air turbine handpiece is used in many cases.
- FIG. 25 depicts an air turbine handpiece 120 for dental use.
- the air turbine handpiece 120 for dental use has a grip part 121 and a head part 122 provided at a tip end portion of the grip part 121.
- An operator performs cutting processing for teeth with holding the grip part 121, for example.
- the air turbine handpiece has a head housing (hereinafter, simply referred to as "housing") having an air supply port and an exhaust port, in which a rotary shaft having a turbine blade, to which compressed air from the air supply port is to be supplied, is rotatably accommodated.
- the rotary shaft is supported to the housing via a rolling bearing so as to be rotatable at high speed. The operator operates the air turbine handpiece while rotating a tool for treatment mounted to the rotary shaft at high speed, thereby cutting the teeth, for example.
- Patent Document 1 discloses an air turbine handpiece in which a rolling bearing is provided with a heat-resistant mechanical seal.
- a pressure of the compressed air is applied, i.e., when the rotary shaft having the turbine blade is rotated, the heat-resistant mechanical seal is elastically deformed so as to contact the rolling bearing, thereby shielding the compressed air.
- lubricant in the rolling bearing is prevented from being leaked by an influence of the compressed air that is to be applied during the use.
- the pressure of the compressed air is not applied, i.e., when the rotary shaft is not rotated, the seal returns to an initial state so as not to be in contact with the rolling bearing. Thereby, upon start of the rotation, a friction resistance between the heat-resistant mechanical seal and the rolling bearing is removed, so that the tool for treatment mounted to the rotary shaft can be smoothly activated.
- Patent Document 1 JP-A-2003-135486
- the air turbine handpiece is used with rotating at ultrahigh speed of about 400,000 min -1 .
- an operation of stopping the rotation i.e., when the supply of the compressed air is stopped, it is required to promptly stop the rotation of the rolling bearing.
- Patent Document 1 discloses a contact shield configured by a seal body and a seal support ring. However, stiffness of the contact shield is high, and a high air pressure is required when the contact shield is used for rotation at ultrahigh speed of about 400,000 min -1 .
- the present invention has been made in view of the above situations, and a first object thereof is to provide a rolling bearing, a bearing unit for an air turbine and an air turbine handpiece for dental use capable of implementing rotation at ultrahigh speed, which is higher than the related art, and prompt stop of the rotation.
- a second object is to provide a rolling bearing, a bearing unit for an air turbine and an air turbine handpiece for dental use capable of implementing rotation at ultrahigh speed with a low air pressure and prompt stop of the rotation.
- the bearing unit for an air turbine and the air turbine handpiece for dental use of the present invention it is possible to implement both the rotation at ultrahigh speed, which is higher than the related art, and the prompt stop of the rotation.
- the bearing unit for an air turbine and the air turbine handpiece for dental use of the present invention since the substantially annular member is configured only by the elastic member and the seal stiffness can be lowered, it is possible to increase the number of revolutions of the rolling bearing with a low air pressure.
- FIG. 1 is a sectional view of main parts of an air turbine handpiece for dental use of a first embodiment.
- a bearing unit 100 for an air turbine is mounted to a head part 201 of an air turbine handpiece 200 for dental use.
- the bearing unit 100 for an air turbine includes a turbine blade 103 configured to rotate with receiving compressed air, a rotary shaft 101 having the turbine blade 103 integrally fixed thereto and capable of mounting a tool (for example, a tool for dental treatment) to an end thereof, and a pair of rolling bearings 1 for an air turbine (hereinafter, referred to as 'rolling bearing') configured to rotatably support the rotary shaft 101 to a housing 105.
- the respective rolling bearings I are supported to the housing 105 via rubber rings 113 mounted to annular concave parts 109, 111 of the housing 105. Also, one rolling bearing I is urged toward the other rolling bearing 1 by a spring washer 115.
- FIG. 2 is a partial sectional view depicting a stop state of the rolling bearing of the first embodiment.
- the rolling bearing 1 is a bearing including an outer ring 10 having an outer ring raceway 10a, an inner ring 20 having an inner ring raceway 20a, a plurality of balls (rolling elements) 3 rollably arranged between the outer ring 10 and the inner ring 20, and a cage 5 configured to rollably hold the plurality of balls 3.
- the rolling bearing is not limited to the shown bearing, and may also be an angular-type bearing.
- the outer ring 10 is held in the housing 105 via the rubber ring 113 shown in FIG. 1 .
- the inner ring 20 is fixed to the rotary shaft 101.
- the cage 5 is a so-called crown-type cage, and a substantially circular ring-shaped rim part 7 is located at a more upstream side with respect to a supply direction of the compressed air than the ball 3, i.e., at a right side in FIG. 2 .
- An arrow P in FIG. 2 indicates a flow direction of the compressed air.
- a circular ring-shaped seal member 30 is provided between the outer ring 10 and the inner ring 20, and is configured to seal a bearing internal space S between an inner peripheral surface 11 of the outer ring 10 and an outer peripheral surface 21 of the inner ring 20 over an entire circumference.
- the seal member 30 consists of an elastic body made only by an elastic material without a metal core.
- An outer peripheral part of the seal member 30 is fixed to a groove portion 13 formed in the inner peripheral surface of the outer ring 10 by a snap ring 40, so that an inner peripheral part thereof can be elastically deformed in an axial direction and a radial direction of the bearing.
- the elastic member configuring the seal member 30 for example, an acryl rubber having Shore A hardness (Japanese Industrial Standards K 6253) of 60 to 90, a fluorine-contained rubber having Shore A hardness of 60 to 90, and the like can be used.
- the seal member 30 is formed with the above material, so that an appropriate elastic characteristic is obtained and durability and wear resistance are also improved.
- the air turbine handpiece for dental use is subjected to high-temperature cleaning/sterilization treatments after the use
- the acryl rubber or fluorine-contained rubber having water resistance and steam (high temperature/high humidity) resistance is preferably used.
- the seal member 30 is provided at a bearing end portion positioned at a more downstream side with respect to the supply direction of the compressed air than the ball 3, i.e., at a left bearing end portion in FIG. 2 . That is, the seal member 30 is provided at one axial end portion of the bearing internal space S opposite to a compressed air supply side (an inlet of the compressed air).
- the inner peripheral surface 11 of the outer ring 10 is formed with the groove portion 13 for fixing therein the seal member 30.
- the seal member 30 is fixed to the groove portion 13 by the snap ring 40.
- a shape of the seal member 30 is not limited to a circular ring shape, and may be another shape inasmuch as the shape is substantially annular, as described later.
- the outer peripheral surface 21 of the inner ring 20 has an inclined surface 23 at a downstream side with respect to the supply direction of the compressed air, i.e., at a left end portion in FIG. 2 .
- the inclined surface 23 is formed to have a conical surface shape inclined so that a diameter changes from large to small toward the downstream side with respect to the axial supply direction of the compressed air.
- FIG. 3 is a sectional view of the seal member 30.
- the seal member 30 has a circular ring-shaped base part 31 extending in the radial direction and an elastically deformable lip part 33 extending from a radially inner end of the base part 31 and inclined to the downstream side with respect to the supply direction of the compressed air toward a radially inner side.
- An inclination angle ⁇ of an inclined surface of the lip part 33 of the seal member 30, which is positioned at the upstream side with respect to the supply direction of the compressed air, relative to the base part 31 is 30° to 80°, preferably 40° to 70°, and more preferably 45° to 65°.
- the inclination angle ⁇ is set to 55° within the above range, a balance between a friction resistance and flow of the compressed air becomes favorable.
- the inclination angle ⁇ is smaller than the above range, a contact resistance excessively increases, and when the inclination angle is greater than the above range, a flow resistance of the compressed air excessively increases, so that intended performance to be described later is not obtained.
- a radially outer end portion of the base part 31 of the seal member 30 is inserted in the groove portion 13 together with the snap ring 40 and is fixed to the groove portion 13.
- the groove portion 13 has a tapered surface 15 inclined to a radially outer side toward an axially inner side, an axially inner surface 17 with which an axial side surface of the base part 31 is in contact at a more axially inner side than the tapered surface 15, and an inner cylinder-shaped groove bottom surface connecting the tapered surface 15 and the axially inner surface 17 each other.
- An outer diameter of the snap ring 40 can be reduced by elastic deformation, such as a C-shaped ring.
- the base part 31 of the seal member 30 and the snap ring 40 are interposed and fixed between the tapered surface 15 and the axially inner surface 17.
- An outer diameter-side end portion of an axially outer side of the snap ring 40 is linearly contacted to the tapered surface 15 along a circumferential direction. In this state, the outer diameter of the snap ring 40 is reduced by the elastic deformation, as compared to a free state.
- a pressing force generated as a result of the elastic deformation presses the tapered surface 15, thereby generating a force of pressing the snap ring 40 toward the radially outer side and a force of pressing the snap ring 40 toward the axially inner side.
- the snap ring 40 may have a circular section, other than a rectangular section.
- the snap ring 40 may be provided with an inclined surface, the groove portion 13 may be formed to have a rectangular section, and a corner portion of the groove portion 13 having the rectangular section may be pressed to the inclined surface of the snap ring 40.
- the lip part 33 is inclined to the downstream side (the axially outer side) with respect to the supply direction of the compressed air toward the radially inner side, and the inclined surface thereof positioned at the upstream side with respect to the supply direction of the compressed air is in contact with the inclined surface 23 of the inner ring 20.
- the inclination angle ⁇ of the inclined surface of the lip part 33 positioned at the upstream side with respect to the supply direction of the compressed air is set smaller than an inclination angle of the inclined surface 23 of the inner ring 20. For this reason, an elastic deformation amount of the lip part 33 increases toward an inner diameter side.
- FIG. 4 is a partial sectional view depicting an operating state of the rolling bearing of the first embodiment.
- the air turbine handpiece 200 for dental use When the air turbine handpiece 200 for dental use is driven and the compressed air is thus supplied to the turbine blade 103, the supplied compressed air is introduced into the bearing internal space S of the bearing unit 100 for an air turbine (refer to FIG. 1 ) configured as described above, and a pressure of the compressed air is applied to the seal member 30. Then, the seal member 30 is elastically deformed toward the downstream side with respect to the flow of the compressed air. As a result, as compared to when the pressure of the compressed air is not applied, a contact area between an inner peripheral surface 35 of the lip part 33 and the inclined surface 23 of the inner ring 20 is reduced. That is, the lip part 33 is in an open state in which the compressed air is enabled to communicate.
- the seal member 30 is configured only by the elastic material without a metal core, the seal member is likely to be elastically deformed, as a whole. For this reason, when the compressed air exceeding a specific pressure is applied to the seal member 30, the inner peripheral part of the seal member 30 is elastically deformed outward in the axial direction, and the contact area between the inclined surface of the lip part 33 positioned at the upstream side with respect to the supply direction of the compressed air and the inclined surface 23 of the inner ring 20 is reduced.
- the inclined surface 23 is provided at the end portion of the outer peripheral surface 21 of the inner ring 20, which is positioned at the downstream side with respect to the supply direction of the compressed air, so that the flow of the compressed air passing between the lip part 33 and the inclined surface 23 becomes smooth and the rotation at ultrahigh speed, which is higher than the related art, can be implemented.
- the inclined surface of the lip part 33 of the seal member 30, which is positioned at the upstream side with respect to the supply direction of the compressed air, is configured to contact the inclined surface 23 of the inner ring 20, slight axial displacement of the lip part 33 can largely lower the friction resistance between the lip part 33 and the inclined surface 23. Also, during the stop, since the contact area between the lip part 33 and the inclined surface 23 is large, the high friction resistance is generated, so that the excellent brake effect is obtained. Also, since the contact area between the lip part 33 and the inclined surface 23 is large, it is possible to obtain the high seal effect during the stop.
- the balance between the rotating speed of the rotary shaft 101 and the brake performance can be optimally set by adjusting the inclination of the inclined surface 23, a thickness of the seal member 30 and the inclination angle of the inclined surface of the lip part 33, which is positioned at the upstream side with respect to the supply direction of the compressed air.
- the rotation at extremely high speed is required upon cutting of teeth, and the prompt rotation stop performance within 2 seconds, preferably one second is required upon the stop. According to the above configuration, since the effects of increasing the rotating speed and shortening the stop time are stably accomplished, it is possible to considerably improve the usability of the air turbine handpiece 200 for dental use.
- the seal member 30 is arranged at one axial end portion of the outer ring 10, which is opposite to the inlet of the compressed air.
- the spray lubrication is performed from between the pair of rolling bearings 1, so that lubricant can be supplied into each rolling bearing 1 from a bearing end portion-side at which the seal member 30 is not arranged.
- the seal member 30 is arranged at the opposite side to the spray-lubrication side, the liquid leakage from each rolling bearing 1 to an outside of the head part 201 is prevented upon the lubrication.
- the air turbine handpiece 200 for dental use is subjected to high-temperature cleaning/sterilization treatments after the use.
- an amount of the lubricant in the rolling bearings 1 is reduced.
- the seal member 30 is arranged only at one axial end portion of the rolling bearing 1, the lubricant can be easily supplied from the other axial end portion. For this reason, it is possible to keep the rolling bearings 1 in a favorable lubrication state all the time, so that it is possible to stably rotate the rotary shaft 101.
- FIG. 5 is a partial sectional view depicting a rolling bearing of a second embodiment.
- the seal member 30A when the compressed air is introduced into the bearing internal space S and the pressure of the compressed air is applied to a seal member 30A, the seal member 30A is in a state where the inclined surface of the lip part 33, which is positioned at the upstream side with respect to the supply direction of the compressed air, and the inclined surface 23 of the inner ring 20 are not completely contacted each other.
- the non-contact state is kept by the compressed air flowing between the lip part 33 and the inclined surface 23.
- the inclined surface of the lip part 33 which is positioned at the upstream side with respect to the supply direction of the compressed air, is in contact with the inclined surface 23 of the inner ring 20 over an entire circumference.
- the seal member 30A configured as described above, when the pressure of the compressed air is applied to the seal member 30A, the friction resistance generated as a result of the contact between the seal member 30A and the inner ring 20 is completely removed, so that it is possible to implement the rotation at ultrahigh speed, which is higher than the first embodiment.
- the other operational effects are similar to the first embodiment.
- FIG. 6 is a partial sectional view depicting a rolling bearing of a third embodiment.
- an inner ring 20A more extends outward in the axial direction than the outer ring 10
- a seal member 30C more protrudes outward in the axial direction than the outer ring 10.
- the inner ring 20A has the inclined surface 23 at an end portion of the outer peripheral surface 21, which is a downstream side with respect to the supply direction of the compressed air, i.e., at one end portion of the outer peripheral surface 21, which is located at the left side in FIG. 6 .
- the inclined surface 23 has a conical surface of which a diameter changes from large to small toward the downstream side with respect to the axial supply direction of the compressed air.
- the seal member 30C is configured so that the inclined surface of the lip part 33 positioned at the upstream side with respect to the supply direction of the compressed air is in contact with the inclined surface 23 of the inner ring 20A at a more axially outer side than the outer ring 10.
- an inclination angle ⁇ 3 of the inclined surface of the lip part 33 which is positioned at the upstream side with respect to the supply direction of the compressed air, from the radial direction can be set greater than the inclination angle ⁇ of the first and second embodiments. For this reason, it is possible to more smoothly perform the operation of opening and closing the lip part 33 by the compressed air.
- the other operational effects are similar to the first and second embodiments.
- FIG. 7 is a partial sectional view depicting a rolling bearing of a fourth embodiment.
- one end portion of the outer peripheral surface 21 of an inner ring 20B which is a downstream side with respect to the supply direction of the compressed air, is formed with a small-diameter part 61.
- the outer peripheral surface 21 is formed with a step surface 67 between a shoulder part 65 connecting to the inner ring raceway 20a and the small-diameter part 61.
- the step surface 67 is configured by a wall surface formed over an entire circumference as a result of the radial cutting.
- a seal member 30D has an elastically deformable flat circular disc shape, and is mounted to the groove portion 13 of the outer ring 10 so that a radially inner part of an upstream surface with respect to the supply direction of the compressed air is in contact with the wall surface of the step surface 67 with being elastically deformed to have the pressing force in the axial direction.
- the seal member 30D has the elastically deformable flat circular disc shape, and the step surface 67 is a wall surface substantially perpendicular to the axial direction.
- the present invention is not limited thereto.
- one or both of the radially inner part of the seal member 30D and the step surface 67 may be slightly inclined from the radial direction.
- the lip part 33 of the seal member 30D is configured to axially contact the step surface 67 of the inner ring 20B, it is possible to reduce a contact pressure between the seal member 30D and the step surface 67, as compared to a configuration where the seal member and the step surface are contacted each other in the radial direction.
- the rolling bearing of the fifth embodiment is similar to the first embodiment, except that a cage 7 is configured as an outer ring guide type.
- the cage is arranged at the outer ring-side, and an inner gap between the outer peripheral surface of the inner ring and an inner peripheral surface of the cage is greater than an outer gap of the outer ring-side.
- the compressed air is directly ejected to the lip part, so that the seal member can be securely elastically deformed even when the supply pressure of the compressed air is relatively low. Thereby, it is possible to perform the operation of opening and closing the seal member by the compressed air more smoothly and in a higher responsiveness manner.
- FIG. 8 is a partial sectional view depicting a rolling bearing of a sixth embodiment.
- a rolling bearing 1E of the sixth embodiment is similar to the first embodiment, except that a shape of the lip part 33 of a seal member 30E is different and at least a part, with which the lip part 33 is in contact, of the outer peripheral surface 21 of an inner ring 20C is a cylindrical surface.
- the lip part 33 of the seal member 30E has a conical shape inclined (in a direction from right to left, in FIG. 8 ) to the downstream side with respect to the supply direction of the compressed air toward the radially inner side. That is, the lip part 33 is inclined outward in the axial direction toward the radially inner side.
- An inner peripheral surface of a radially inner periphery end of the lip part 33 of the seal member 30E is configured as an inner cylinder surface parallel with the axis.
- the inner cylinder surface, which is the inner peripheral surface of the lip part 33, is in contact with the cylindrical surface of the outer peripheral surface 21 of the inner ring 20C. In this way, the seal member 30E is configured to seal the bearing internal space S between the inner peripheral surface 11 of the outer ring 10 and the outer peripheral surface 21 of the inner ring 20C.
- FIGS. 8 and 9 depict the different shapes of the lip part 33.
- the lip part 33 may have a thickness that is uniform toward the radially inner side, as shown in FIG. 8 , or may have a thickness that gradually decreases toward the radially inner side, as shown in FIG. 9 .
- FIG. 10 is a partial sectional view depicting an operating state of the rolling bearing of the sixth embodiment.
- the arrow P in FIG. 10 indicates the flow direction of the compressed air.
- the compressed air When the compressed air is supplied to the turbine blade so as to drive the air turbine handpiece, the compressed air flows in the bearing internal space S from the right toward the left in FIG. 10 .
- the compressed air is applied to the seal member 30E, thereby elastically deforming the lip part 33 so that an inner diameter thereof increases. Accordingly, when the compressed air is applied, the contact area between the inner peripheral surface of the radially inner periphery end of the lip part 33 and the outer peripheral surface 21 of the inner ring 20A is reduced, as compared to when the compressed air is not applied.
- the inner peripheral surface of the radially inner periphery end of the lip part 33 is not in contact with the outer peripheral surface 21 of the inner ring 20C, and the contact area is zero.
- the lip part 33 is in an opened state. Also, like an example of FIG. 11 , a configuration is also possible in which when the compressed air is applied, the inner peripheral surface of the radially inner periphery end of the lip part 33 and the outer peripheral surface 21 of the inner ring 20C are in contact with each other and the contact area between the inner peripheral surface 35 of the lip part 33 and the outer peripheral surface 21 of the inner ring 20C is reduced, as compared to when the compressed air is not applied.
- the seal member 30E since the seal member 30E is configured only by the elastic material without a metal core, the seal member is likely to be elastically deformed, as a whole. For this reason, when the compressed air exceeding a specific pressure is applied to the seal member 30E, the inner peripheral part of the seal member 30E is elastically deformed outward in the axial direction, and the contact area between the inner peripheral surface of the lip part 33 and the inclined surface 23 of the inner ring 20 is reduced.
- the lip part 33 returns to the state as shown in FIG. 8 .
- the inner peripheral surface of the lip part 33 is surface-contacted to the outer peripheral surface 21 of the inner ring 20C with generating the pressing force. That is, the lip part 33 is in a closed state.
- the lip part 33 functions as a brake of the inner ring 20C and the rotary shaft 101 (refer to FIG. 1 ), to which the inner ring 20C is fixed, so that it is possible to promptly stop the rotary shaft 101.
- the lip part 33 is formed to have an inclined shape that is inclined to the downstream side with respect to the supply direction of the compressed air toward the radially inner side and can be thus easily elastically deformed by the compressed air. Therefore, it is possible to perform the operation of opening and closing the lip part 33 by the compressed air with good sensitivity.
- the inclination angle ⁇ of the lip part 33 of the seal member 30E is preferably set to 35° to 55°.
- the outer peripheral surface 21 of the inner ring 20C is configured as the cylindrical surface, it is possible to increase the contact area between the outer peripheral surface 21 of the inner ring 20C and the inner peripheral surface of the lip part 33, thereby improving the brake function of the lip part 33.
- the inner peripheral surface of the lip part 33 is surface-contacted to the cylindrical outer peripheral surface 21 of the inner ring 20C, it is possible to further improve the brake function of the lip part 33.
- the radially inner peripheral surface of the lip part 33 may have a substantially triangular section.
- the brake performance is lowered.
- FIG. 12 is a partial sectional view depicting a rolling bearing of a seventh embodiment.
- an inner ring 20D of a rolling bearing 1F may more extend outward in the axial direction than the outer ring 10 and a seal member 30F may more extend outward in the axial direction than the outer ring 10, inasmuch as the seal performance is obtained.
- the inner peripheral surface of the lip part 33 of the seal member 30F is in contact with the outer peripheral surface 21 of the inner ring 20D at the more axially outer side than the outer ring 10. According to this configuration, since it is possible to largely incline the lip part 33, it is possible to more easily perform the operation of opening and closing the lip part 33 by the compressed air.
- the present invention is not limited to the above embodiments, and can be appropriately modified and improved.
- the cage 5 that is used for the rolling bearing 1 of the first to seventh embodiments is configured so that the rim part 7 provided at one end-side thereof is arranged at the more upstream side with respect to the supply direction of the compressed air than the ball 3.
- the present invention is not limited thereto.
- the rim part 7 may be arranged at the seal member-side of the axially opposite side.
- the seal member is arranged only at one axial end-side of the rolling bearing 1, the groove portion 13 of the outer ring 10, the inclined surface 23 of the inner rings 20, 20A of the first to fifth embodiments, and the step surface 67 are formed only at one axial end-side.
- the present invention is not limited thereto.
- they may also be symmetrically formed at the other axial end-side.
- one of a pair of groove portions 13 is not used, and in the configurations of the first to fifth embodiments, a pair of inclined surfaces or steps is not used. In this case, in a process of assembling the rolling bearing, it is not necessary to consider a mounting direction, so that it is possible to simplify the operation process.
- the lip part of the seal member may have a thickness that is constant or gradually decreases toward the radially inner side.
- a shape of the inner diameter-side end portion of the lip part 33 of the seal member may be substantially elliptical or triangular, as shown in FIGS. 13 and 14 .
- the other examples of the seal member 30 to be described below can also be applied to the seal members 30A, 30B, 30C, 30D, 30E, 30F.
- the inner diameter-side end portion of the lip part 33 may be provided with at least one ventilation hole 41, as shown in FIG. 15 , or may be provided with at least one slit 43, as shown in FIGS. 16 to 18 .
- FIG. 15 the example where one circular ventilation hole 41 is provided is shown.
- the two or more ventilation holes 41 may be provided, and the shape of the ventilation hole 41 is not limited to the circular shape.
- FIGS. 16 to 18 show the examples where the two slits 43, the four slits 43 and the eight slits 43 are respectively provided with being equidistantly spaced in a circumferential direction.
- the numbers and circumferential intervals of the slits 43 are not limited thereto.
- the inner diameter-side end portion of the lip part 33 may be notched continuously in the circumferential direction and the inner diameter-side end portion of the lip part 33 may be in partial contact with the outer peripheral surface 21 of the inner ring 20.
- FIG. 22A is a sectional view taken along a line A-A of FIGS. 19 to 21
- FIG. 22B is a sectional view taken along a line B-B of FIGS. 19 to 21 .
- the ball bearing is used as the rolling bearing.
- the other rolling bearing such as a roller bearing can also be used.
- the rolling bearing is an inner ring rotation type and the seal member is fixed to the outer ring.
- a configuration where the seal member is fixed to the inner ring and is in contact with the outer ring is also possible.
- a configuration is possible in which the shape of the cage is changed to increase the bearing width, as compared to the above embodiments.
- the rolling bearing of the present invention may be an angular-type rolling bearing.
- FIG. 23 is a partial sectional view of an angular-type rolling bearing having a counterbore 81 formed in an outer ring 10A.
- the inclined surface 23 and the seal member 30 of the rolling bearing 1 of the first embodiment are applied to the outer ring 10A and the inner ring 20, for example.
- FIG. 24 is a partial sectional view of an angular-type rolling bearing having a counterbore 83 formed in an inner ring. Also in this case, the inclined surface 23 and the seal member 30 of the rolling bearing 1 of the first embodiment are applied to the outer ring 10 and the inner ring 20E.
- FIGS. 23 and 24 even with the angular-type rolling bearing, the similar operational effects to the above-described operational effects are accomplished. Meanwhile, FIGS. 23 and 24 just show the examples, and the rolling bearings 1A to 1F of the other embodiments can be configured by the above angular-type rolling bearing or by another angular-type rolling bearing.
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- Health & Medical Sciences (AREA)
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Oral & Maxillofacial Surgery (AREA)
- Mechanical Engineering (AREA)
- Life Sciences & Earth Sciences (AREA)
- Veterinary Medicine (AREA)
- Public Health (AREA)
- General Health & Medical Sciences (AREA)
- Animal Behavior & Ethology (AREA)
- Epidemiology (AREA)
- Dentistry (AREA)
- Sustainable Development (AREA)
- Sustainable Energy (AREA)
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- Combustion & Propulsion (AREA)
- Rolling Contact Bearings (AREA)
- Dental Tools And Instruments Or Auxiliary Dental Instruments (AREA)
- Sealing Of Bearings (AREA)
Abstract
Description
- The present invention relates to a rolling bearing, a bearing unit for an air turbine, and an air turbine handpiece for dental use.
- For dental treatment, a small and lightweight air turbine handpiece is used in many cases.
- For example,
FIG. 25 depicts anair turbine handpiece 120 for dental use. Theair turbine handpiece 120 for dental use has agrip part 121 and ahead part 122 provided at a tip end portion of thegrip part 121. An operator performs cutting processing for teeth with holding thegrip part 121, for example. - The air turbine handpiece has a head housing (hereinafter, simply referred to as "housing") having an air supply port and an exhaust port, in which a rotary shaft having a turbine blade, to which compressed air from the air supply port is to be supplied, is rotatably accommodated. The rotary shaft is supported to the housing via a rolling bearing so as to be rotatable at high speed. The operator operates the air turbine handpiece while rotating a tool for treatment mounted to the rotary shaft at high speed, thereby cutting the teeth, for example.
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Patent Document 1 discloses an air turbine handpiece in which a rolling bearing is provided with a heat-resistant mechanical seal. When a pressure of the compressed air is applied, i.e., when the rotary shaft having the turbine blade is rotated, the heat-resistant mechanical seal is elastically deformed so as to contact the rolling bearing, thereby shielding the compressed air. Thereby, lubricant in the rolling bearing is prevented from being leaked by an influence of the compressed air that is to be applied during the use. On the other hand, when the pressure of the compressed air is not applied, i.e., when the rotary shaft is not rotated, the seal returns to an initial state so as not to be in contact with the rolling bearing. Thereby, upon start of the rotation, a friction resistance between the heat-resistant mechanical seal and the rolling bearing is removed, so that the tool for treatment mounted to the rotary shaft can be smoothly activated. - Patent Document 1:
JP-A-2003-135486 - The air turbine handpiece is used with rotating at ultrahigh speed of about 400,000 min-1. In the meantime, when an operation of stopping the rotation is performed, i.e., when the supply of the compressed air is stopped, it is required to promptly stop the rotation of the rolling bearing.
- However, when the pressure of the compressed air is applied to the heat-resistant mechanical seal of the rolling bearing disclosed in
Patent Document 1, i.e., when the rotary shaft having the turbine blade mounted thereto is rotated, the heat-resistant mechanical seal is contacted to the rolling bearing configured to support the rotary shaft, so that a resistance of the rolling bearing is increased. For this reason, the rolling bearing is not suitable for rotation at ultrahigh speed of about 400,000 min-1. Also, when the supply of the compressed air is stopped, the heat-resistant mechanical seal is not contacted to the rolling bearing, so that the friction resistance of the rolling bearing is reduced. Accordingly, it is disadvantageous to promptly stop the rolling bearing. Also,Patent Document 1 discloses a contact shield configured by a seal body and a seal support ring. However, stiffness of the contact shield is high, and a high air pressure is required when the contact shield is used for rotation at ultrahigh speed of about 400,000 min-1. - The present invention has been made in view of the above situations, and a first object thereof is to provide a rolling bearing, a bearing unit for an air turbine and an air turbine handpiece for dental use capable of implementing rotation at ultrahigh speed, which is higher than the related art, and prompt stop of the rotation.
- Also, a second object is to provide a rolling bearing, a bearing unit for an air turbine and an air turbine handpiece for dental use capable of implementing rotation at ultrahigh speed with a low air pressure and prompt stop of the rotation.
- The above objects of the present invention are accomplished by following configurations.
- (1) A bearing unit for an air turbine including:
- a turbine blade configured to rotate with receiving compressed air,
- a rotary shaft having the turbine blade integrally fixed thereto and capable of mounting a tool thereto, and
- a rolling bearing configured to rotatably support the rotary shaft to a housing,
- an outer ring fixed to the housing,
- an inner ring fixed to the rotary shaft,
- a plurality of rolling elements rollably arranged between the outer ring and the inner ring, and
- a seal member fixed to an inner peripheral surface of the outer ring and configured to seal a bearing internal space between the outer ring and the inner ring,
wherein the seal member is configured only by an elastic material without a metal core, and has a base part extending in a radial direction and a lip part extending from a radially inner end of the base part and inclined to the downstream side with respect to the supply direction of the compressed air toward a radially inner side,
wherein when the compressed air is not applied, an inclined surface, which is positioned at an upstream side with respect to the supply direction of the compressed air, of the lip part of the seal member is in contact with the inclined surface of the inner ring, and
wherein when the compressed air is applied, a contact area between the inclined surface, which is positioned at the upstream side with respect to the supply direction of the compressed air, of the lip part of the seal member and the inclined surface of the inner ring becomes smaller, as compared to when the compressed air is not applied. - (2) A bearing unit for an air turbine including:
- a turbine blade configured to rotate with receiving compressed air,
- a rotary shaft having the turbine blade integrally fixed thereto and capable of mounting a tool thereto, and
- a rolling bearing configured to rotatably support the rotary shaft to a housing,
- an outer ring fixed to the housing,
- an inner ring fixed to the rotary shaft,
- a plurality of rolling elements rollably arranged between the outer ring and the inner ring, and
- a seal member fixed to an inner peripheral surface of the outer ring and configured to seal a bearing internal space between the outer ring and the inner ring,
wherein the seal member is configured only by an elastic material without a metal core, and has a base part extending in a radial direction and the lip part extending from a radially inner end of the base part and inclined to a downstream side with respect to a supply direction of the compressed air toward a radially inner side,
wherein when the compressed air is not applied, an inner peripheral surface of the lip part of the seal member is in contact with the cylindrical surface of the inner ring, and
wherein when the compressed air is applied, a contact area between the inner peripheral surface of the lip part of the seal member and the cylindrical surface of the inner ring becomes smaller, as compared to when the compressed air is not applied. - (3) The bearing unit for an air turbine according to (1) or (2), wherein when the compressed air is applied, the seal member is not in contact with the outer peripheral surface of the inner ring.
- (4) An air turbine handpiece for dental use including the bearing unit for an air turbine according to one of (1) to (3).
- According to the rolling bearing, the bearing unit for an air turbine and the air turbine handpiece for dental use of the present invention, it is possible to implement both the rotation at ultrahigh speed, which is higher than the related art, and the prompt stop of the rotation.
- Also, according to the rolling bearing, the bearing unit for an air turbine and the air turbine handpiece for dental use of the present invention, since the substantially annular member is configured only by the elastic member and the seal stiffness can be lowered, it is possible to increase the number of revolutions of the rolling bearing with a low air pressure.
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FIG. 1 is a sectional view of main parts of an air turbine handpiece for dental use of a first embodiment. -
FIG. 2 is a partial sectional view depicting a stop state of a rolling bearing of the first embodiment. -
FIG. 3 is a sectional view of a seal member. -
FIG. 4 is a partial sectional view depicting an operating state of the rolling bearing of the first embodiment. -
FIG. 5 is a partial sectional view depicting a rolling bearing of a second embodiment. -
FIG. 6 is a partial sectional view depicting a rolling bearing of a third embodiment. -
FIG. 7 is a partial sectional view depicting a rolling bearing of a fourth embodiment. -
FIG. 8 is a partial sectional view depicting a rolling bearing of a sixth embodiment. -
FIG. 9 is a sectional view for illustrating a contact angle of the seal member shown inFIG. 8 . -
FIG. 10 is a partial sectional view depicting a rolling bearing of the sixth embodiment. -
FIG. 11 is a partial sectional view depicting an operating state of a rolling bearing of a modified embodiment of the sixth embodiment. -
FIG. 12 is a partial sectional view depicting a rolling bearing of a seventh embodiment. -
FIG. 13 is a front view of a seal member, exemplifying another embodiment. -
FIG. 14 is a front view of a seal member, exemplifying another embodiment. -
FIG. 15 is a front view of a seal member, exemplifying another embodiment. -
FIG. 16 is a front view of a seal member, exemplifying another embodiment. -
FIG. 17 is a front view of a seal member, exemplifying another embodiment. -
FIG. 18 is a front view of a seal member, exemplifying another embodiment. -
FIG. 19 is a front view of a seal member, exemplifying another embodiment. -
FIG. 20 is a front view of a seal member, exemplifying another embodiment. -
FIG. 21 is a front view of a seal member, exemplifying another embodiment. -
FIG. 22A is a sectional view taken along a line A-A ofFIGS. 19 to 21 . -
FIG. 22B is a sectional view taken along a line B-B ofFIGS. 19 to 21 . -
FIG. 23 is a partial sectional view of an angular-type rolling bearing having a counterbore formed in an outer ring. -
FIG. 24 is a partial sectional view of an angular-type rolling bearing having a counterbore formed in an inner ring. -
FIG. 25 is a schematic side view of an air turbine handpiece for dental use. - Hereinafter, embodiments of a rolling bearing for an air turbine and a bearing unit for an air turbine of the present invention will be described in detail with reference to the drawings. Meanwhile, in the below, an example where the bearing unit for an air turbine of the present invention is applied to an air turbine handpiece for dental use will be described. However, the present invention can be applied to other utilities, for example, a home electronics motor, as well.
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FIG. 1 is a sectional view of main parts of an air turbine handpiece for dental use of a first embodiment. - A bearing
unit 100 for an air turbine is mounted to ahead part 201 of anair turbine handpiece 200 for dental use. Thebearing unit 100 for an air turbine includes aturbine blade 103 configured to rotate with receiving compressed air, arotary shaft 101 having theturbine blade 103 integrally fixed thereto and capable of mounting a tool (for example, a tool for dental treatment) to an end thereof, and a pair of rollingbearings 1 for an air turbine (hereinafter, referred to as 'rolling bearing') configured to rotatably support therotary shaft 101 to ahousing 105. - The respective rolling bearings I are supported to the
housing 105 via rubber rings 113 mounted to annularconcave parts housing 105. Also, one rolling bearing I is urged toward the other rollingbearing 1 by aspring washer 115. -
FIG. 2 is a partial sectional view depicting a stop state of the rolling bearing of the first embodiment. - The rolling
bearing 1 is a bearing including anouter ring 10 having anouter ring raceway 10a, aninner ring 20 having aninner ring raceway 20a, a plurality of balls (rolling elements) 3 rollably arranged between theouter ring 10 and theinner ring 20, and acage 5 configured to rollably hold the plurality ofballs 3. In the meantime, the rolling bearing is not limited to the shown bearing, and may also be an angular-type bearing. Theouter ring 10 is held in thehousing 105 via therubber ring 113 shown inFIG. 1 . Theinner ring 20 is fixed to therotary shaft 101. Thecage 5 is a so-called crown-type cage, and a substantially circular ring-shapedrim part 7 is located at a more upstream side with respect to a supply direction of the compressed air than theball 3, i.e., at a right side inFIG. 2 . An arrow P inFIG. 2 indicates a flow direction of the compressed air. - A circular ring-shaped
seal member 30 is provided between theouter ring 10 and theinner ring 20, and is configured to seal a bearing internal space S between an innerperipheral surface 11 of theouter ring 10 and an outerperipheral surface 21 of theinner ring 20 over an entire circumference. Theseal member 30 consists of an elastic body made only by an elastic material without a metal core. An outer peripheral part of theseal member 30 is fixed to agroove portion 13 formed in the inner peripheral surface of theouter ring 10 by asnap ring 40, so that an inner peripheral part thereof can be elastically deformed in an axial direction and a radial direction of the bearing. - As the elastic member configuring the
seal member 30, for example, an acryl rubber having Shore A hardness (Japanese Industrial Standards K 6253) of 60 to 90, a fluorine-contained rubber having Shore A hardness of 60 to 90, and the like can be used. Theseal member 30 is formed with the above material, so that an appropriate elastic characteristic is obtained and durability and wear resistance are also improved. - Particularly, since the air turbine handpiece for dental use is subjected to high-temperature cleaning/sterilization treatments after the use, the acryl rubber or fluorine-contained rubber having water resistance and steam (high temperature/high humidity) resistance is preferably used.
- The
seal member 30 is provided at a bearing end portion positioned at a more downstream side with respect to the supply direction of the compressed air than theball 3, i.e., at a left bearing end portion inFIG. 2 . That is, theseal member 30 is provided at one axial end portion of the bearing internal space S opposite to a compressed air supply side (an inlet of the compressed air). The innerperipheral surface 11 of theouter ring 10 is formed with thegroove portion 13 for fixing therein theseal member 30. Theseal member 30 is fixed to thegroove portion 13 by thesnap ring 40. A shape of theseal member 30 is not limited to a circular ring shape, and may be another shape inasmuch as the shape is substantially annular, as described later. - The outer
peripheral surface 21 of theinner ring 20 has aninclined surface 23 at a downstream side with respect to the supply direction of the compressed air, i.e., at a left end portion inFIG. 2 . Theinclined surface 23 is formed to have a conical surface shape inclined so that a diameter changes from large to small toward the downstream side with respect to the axial supply direction of the compressed air. -
FIG. 3 is a sectional view of theseal member 30. - The
seal member 30 has a circular ring-shapedbase part 31 extending in the radial direction and an elasticallydeformable lip part 33 extending from a radially inner end of thebase part 31 and inclined to the downstream side with respect to the supply direction of the compressed air toward a radially inner side. An inclination angle θ of an inclined surface of thelip part 33 of theseal member 30, which is positioned at the upstream side with respect to the supply direction of the compressed air, relative to thebase part 31 is 30° to 80°, preferably 40° to 70°, and more preferably 45° to 65°. For example, when the inclination angle θ is set to 55° within the above range, a balance between a friction resistance and flow of the compressed air becomes favorable. When the inclination angle θ is smaller than the above range, a contact resistance excessively increases, and when the inclination angle is greater than the above range, a flow resistance of the compressed air excessively increases, so that intended performance to be described later is not obtained. - As shown in
FIG. 2 , a radially outer end portion of thebase part 31 of theseal member 30 is inserted in thegroove portion 13 together with thesnap ring 40 and is fixed to thegroove portion 13. Thegroove portion 13 has a taperedsurface 15 inclined to a radially outer side toward an axially inner side, an axiallyinner surface 17 with which an axial side surface of thebase part 31 is in contact at a more axially inner side than the taperedsurface 15, and an inner cylinder-shaped groove bottom surface connecting the taperedsurface 15 and the axiallyinner surface 17 each other. An outer diameter of thesnap ring 40 can be reduced by elastic deformation, such as a C-shaped ring. Thebase part 31 of theseal member 30 and thesnap ring 40 are interposed and fixed between thetapered surface 15 and the axiallyinner surface 17. An outer diameter-side end portion of an axially outer side of thesnap ring 40 is linearly contacted to the taperedsurface 15 along a circumferential direction. In this state, the outer diameter of thesnap ring 40 is reduced by the elastic deformation, as compared to a free state. A pressing force generated as a result of the elastic deformation presses the taperedsurface 15, thereby generating a force of pressing thesnap ring 40 toward the radially outer side and a force of pressing thesnap ring 40 toward the axially inner side. The force of pressing thesnap ring 40 toward the axially inner side presses theseal member 30 toward the axiallyinner surface 17, so that theseal member 30 is fixed to theouter ring 10. In the meantime, thesnap ring 40 may have a circular section, other than a rectangular section. Also, thesnap ring 40 may be provided with an inclined surface, thegroove portion 13 may be formed to have a rectangular section, and a corner portion of thegroove portion 13 having the rectangular section may be pressed to the inclined surface of thesnap ring 40. - The
lip part 33 is inclined to the downstream side (the axially outer side) with respect to the supply direction of the compressed air toward the radially inner side, and the inclined surface thereof positioned at the upstream side with respect to the supply direction of the compressed air is in contact with theinclined surface 23 of theinner ring 20. The inclination angle θ of the inclined surface of thelip part 33 positioned at the upstream side with respect to the supply direction of the compressed air is set smaller than an inclination angle of theinclined surface 23 of theinner ring 20. For this reason, an elastic deformation amount of thelip part 33 increases toward an inner diameter side. -
FIG. 4 is a partial sectional view depicting an operating state of the rolling bearing of the first embodiment. - When the
air turbine handpiece 200 for dental use is driven and the compressed air is thus supplied to theturbine blade 103, the supplied compressed air is introduced into the bearing internal space S of thebearing unit 100 for an air turbine (refer toFIG. 1 ) configured as described above, and a pressure of the compressed air is applied to theseal member 30. Then, theseal member 30 is elastically deformed toward the downstream side with respect to the flow of the compressed air. As a result, as compared to when the pressure of the compressed air is not applied, a contact area between an innerperipheral surface 35 of thelip part 33 and theinclined surface 23 of theinner ring 20 is reduced. That is, thelip part 33 is in an open state in which the compressed air is enabled to communicate. - Since the
seal member 30 is configured only by the elastic material without a metal core, the seal member is likely to be elastically deformed, as a whole. For this reason, when the compressed air exceeding a specific pressure is applied to theseal member 30, the inner peripheral part of theseal member 30 is elastically deformed outward in the axial direction, and the contact area between the inclined surface of thelip part 33 positioned at the upstream side with respect to the supply direction of the compressed air and theinclined surface 23 of theinner ring 20 is reduced. - Like this, in the above configuration, even when the supply pressure of the compressed air is relatively low, the
lip part 33 of theseal member 30 is securely elastically deformed, so that the contact area can be reduced. - Thereby, it is possible to perform smooth activation of an air turbine, to reduce the friction resistance between the
seal member 30 and theinner ring 20, and to implement rotation of therotary shaft 101 at ultrahigh speed of about 400,000 min-1. Also, theinclined surface 23 is provided at the end portion of the outerperipheral surface 21 of theinner ring 20, which is positioned at the downstream side with respect to the supply direction of the compressed air, so that the flow of the compressed air passing between thelip part 33 and theinclined surface 23 becomes smooth and the rotation at ultrahigh speed, which is higher than the related art, can be implemented. - On the other hand, when the driving of the
air turbine handpiece 200 for dental use is stopped and the supply of the compressed air to theturbine blade 103 is thus stopped, the pressure of the compressed air being applied to thelip part 33 is reduced. Then, the inclined surface of thelip part 33, which is positioned at the upstream side with respect to the supply direction of the compressed air, is surface-contacted to theinclined surface 23 of theinner ring 20 while generating the pressing force. Thereby, thelip part 33 functions as a brake of theinner ring 20. - Also, since the inclined surface of the
lip part 33 of theseal member 30, which is positioned at the upstream side with respect to the supply direction of the compressed air, is configured to contact theinclined surface 23 of theinner ring 20, slight axial displacement of thelip part 33 can largely lower the friction resistance between thelip part 33 and theinclined surface 23. Also, during the stop, since the contact area between thelip part 33 and theinclined surface 23 is large, the high friction resistance is generated, so that the excellent brake effect is obtained. Also, since the contact area between thelip part 33 and theinclined surface 23 is large, it is possible to obtain the high seal effect during the stop. That is, it is possible to reduce the contact pressure with the pressure of the compressed air lower than the conventional structure, and to implement both the additional improvement on the rotating speed of therotary shaft 101 and the shortening of the stop time. The balance between the rotating speed of therotary shaft 101 and the brake performance can be optimally set by adjusting the inclination of theinclined surface 23, a thickness of theseal member 30 and the inclination angle of the inclined surface of thelip part 33, which is positioned at the upstream side with respect to the supply direction of the compressed air. - Particularly, for the
air turbine handpiece 200 for dental use, the rotation at extremely high speed is required upon cutting of teeth, and the prompt rotation stop performance within 2 seconds, preferably one second is required upon the stop. According to the above configuration, since the effects of increasing the rotating speed and shortening the stop time are stably accomplished, it is possible to considerably improve the usability of theair turbine handpiece 200 for dental use. - When driving the
air turbine handpiece 200 for dental use, the compressed air is difficult to be leaked from an inside of the bearing, so that a noise is reduced upon the driving and the high quietness is thus obtained. - Also, as shown in
FIG. 1 , in the pair of rolling bearings I arranged to therotary shaft 101, theseal member 30 is arranged at one axial end portion of theouter ring 10, which is opposite to the inlet of the compressed air. Thereby, the spray lubrication is performed from between the pair of rollingbearings 1, so that lubricant can be supplied into each rollingbearing 1 from a bearing end portion-side at which theseal member 30 is not arranged. Also, since theseal member 30 is arranged at the opposite side to the spray-lubrication side, the liquid leakage from each rollingbearing 1 to an outside of thehead part 201 is prevented upon the lubrication. - In general, the
air turbine handpiece 200 for dental use is subjected to high-temperature cleaning/sterilization treatments after the use. By the treatments, an amount of the lubricant in the rollingbearings 1 is reduced. However, since theseal member 30 is arranged only at one axial end portion of the rollingbearing 1, the lubricant can be easily supplied from the other axial end portion. For this reason, it is possible to keep the rollingbearings 1 in a favorable lubrication state all the time, so that it is possible to stably rotate therotary shaft 101. - Subsequently, a second embodiment of the
bearing unit 100 for an air turbine is described. In the below, the same members and parts as the first embodiment are denoted with the same reference numerals, so that the descriptions thereof are simplified or omitted. -
FIG. 5 is a partial sectional view depicting a rolling bearing of a second embodiment. - In the second embodiment, when the compressed air is introduced into the bearing internal space S and the pressure of the compressed air is applied to a
seal member 30A, theseal member 30A is in a state where the inclined surface of thelip part 33, which is positioned at the upstream side with respect to the supply direction of the compressed air, and theinclined surface 23 of theinner ring 20 are not completely contacted each other. The non-contact state is kept by the compressed air flowing between thelip part 33 and theinclined surface 23. - On the other hand, when the pressure of the compressed air is not applied to the
seal member 30A, the inclined surface of thelip part 33, which is positioned at the upstream side with respect to the supply direction of the compressed air, is in contact with theinclined surface 23 of theinner ring 20 over an entire circumference. - According to the
seal member 30A configured as described above, when the pressure of the compressed air is applied to theseal member 30A, the friction resistance generated as a result of the contact between theseal member 30A and theinner ring 20 is completely removed, so that it is possible to implement the rotation at ultrahigh speed, which is higher than the first embodiment. The other operational effects are similar to the first embodiment. - Subsequently, a third embodiment of the
bearing unit 100 for an air turbine is described. -
FIG. 6 is a partial sectional view depicting a rolling bearing of a third embodiment. - In a rolling bearing 1C of the third embodiment, an
inner ring 20A more extends outward in the axial direction than theouter ring 10, and aseal member 30C more protrudes outward in the axial direction than theouter ring 10. - Like the first and second embodiments, the
inner ring 20A has theinclined surface 23 at an end portion of the outerperipheral surface 21, which is a downstream side with respect to the supply direction of the compressed air, i.e., at one end portion of the outerperipheral surface 21, which is located at the left side inFIG. 6 . Theinclined surface 23 has a conical surface of which a diameter changes from large to small toward the downstream side with respect to the axial supply direction of the compressed air. - Also, the
seal member 30C is configured so that the inclined surface of thelip part 33 positioned at the upstream side with respect to the supply direction of the compressed air is in contact with theinclined surface 23 of theinner ring 20A at a more axially outer side than theouter ring 10. - According to the above configuration, an inclination angle θ3 of the inclined surface of the
lip part 33, which is positioned at the upstream side with respect to the supply direction of the compressed air, from the radial direction can be set greater than the inclination angle θ of the first and second embodiments. For this reason, it is possible to more smoothly perform the operation of opening and closing thelip part 33 by the compressed air. The other operational effects are similar to the first and second embodiments. - Subsequently, a fourth embodiment of the
bearing unit 100 for an air turbine is described. -
FIG. 7 is a partial sectional view depicting a rolling bearing of a fourth embodiment. - In a rolling bearing 1D of the fourth embodiment, one end portion of the outer
peripheral surface 21 of aninner ring 20B, which is a downstream side with respect to the supply direction of the compressed air, is formed with a small-diameter part 61. The outerperipheral surface 21 is formed with astep surface 67 between ashoulder part 65 connecting to theinner ring raceway 20a and the small-diameter part 61. Thestep surface 67 is configured by a wall surface formed over an entire circumference as a result of the radial cutting. - A
seal member 30D has an elastically deformable flat circular disc shape, and is mounted to thegroove portion 13 of theouter ring 10 so that a radially inner part of an upstream surface with respect to the supply direction of the compressed air is in contact with the wall surface of thestep surface 67 with being elastically deformed to have the pressing force in the axial direction. In the shown example, theseal member 30D has the elastically deformable flat circular disc shape, and thestep surface 67 is a wall surface substantially perpendicular to the axial direction. However, the present invention is not limited thereto. For example, one or both of the radially inner part of theseal member 30D and thestep surface 67 may be slightly inclined from the radial direction. - According to the above configuration, since the
lip part 33 of theseal member 30D is configured to axially contact thestep surface 67 of theinner ring 20B, it is possible to reduce a contact pressure between theseal member 30D and thestep surface 67, as compared to a configuration where the seal member and the step surface are contacted each other in the radial direction. Thereby, since it is possible to simply process theseal member 30D and theinner ring 20B, it is possible to save the manufacturing cost and to accomplish the similar effects to the first to third embodiments. - Subsequently, a fifth embodiment of the
bearing unit 100 for an air turbine is described. - The rolling bearing of the fifth embodiment is similar to the first embodiment, except that a
cage 7 is configured as an outer ring guide type. - According to the above configuration, the cage is arranged at the outer ring-side, and an inner gap between the outer peripheral surface of the inner ring and an inner peripheral surface of the cage is greater than an outer gap of the outer ring-side. Thus, when the compressed air is introduced into the bearing internal space, the compressed air flows toward the seal member mainly through the inner gap, which is a radially inner space of the plurality of balls (rolling elements) arranged between the outer ring and the inner ring, and is ejected to the lip part of the seal member.
- The compressed air is directly ejected to the lip part, so that the seal member can be securely elastically deformed even when the supply pressure of the compressed air is relatively low. Thereby, it is possible to perform the operation of opening and closing the seal member by the compressed air more smoothly and in a higher responsiveness manner.
- Subsequently, a sixth embodiment of the
bearing unit 100 for an air turbine is described. -
FIG. 8 is a partial sectional view depicting a rolling bearing of a sixth embodiment. - A rolling
bearing 1E of the sixth embodiment is similar to the first embodiment, except that a shape of thelip part 33 of aseal member 30E is different and at least a part, with which thelip part 33 is in contact, of the outerperipheral surface 21 of aninner ring 20C is a cylindrical surface. - The
lip part 33 of theseal member 30E has a conical shape inclined (in a direction from right to left, inFIG. 8 ) to the downstream side with respect to the supply direction of the compressed air toward the radially inner side. That is, thelip part 33 is inclined outward in the axial direction toward the radially inner side. An inner peripheral surface of a radially inner periphery end of thelip part 33 of theseal member 30E is configured as an inner cylinder surface parallel with the axis. The inner cylinder surface, which is the inner peripheral surface of thelip part 33, is in contact with the cylindrical surface of the outerperipheral surface 21 of theinner ring 20C. In this way, theseal member 30E is configured to seal the bearing internal space S between the innerperipheral surface 11 of theouter ring 10 and the outerperipheral surface 21 of theinner ring 20C. - In the meantime,
FIGS. 8 and9 depict the different shapes of thelip part 33. Thelip part 33 may have a thickness that is uniform toward the radially inner side, as shown inFIG. 8 , or may have a thickness that gradually decreases toward the radially inner side, as shown inFIG. 9 . -
FIG. 10 is a partial sectional view depicting an operating state of the rolling bearing of the sixth embodiment. The arrow P inFIG. 10 indicates the flow direction of the compressed air. - When the compressed air is supplied to the turbine blade so as to drive the air turbine handpiece, the compressed air flows in the bearing internal space S from the right toward the left in
FIG. 10 . The compressed air is applied to theseal member 30E, thereby elastically deforming thelip part 33 so that an inner diameter thereof increases. Accordingly, when the compressed air is applied, the contact area between the inner peripheral surface of the radially inner periphery end of thelip part 33 and the outerperipheral surface 21 of theinner ring 20A is reduced, as compared to when the compressed air is not applied. In the example ofFIG. 10 , the inner peripheral surface of the radially inner periphery end of thelip part 33 is not in contact with the outerperipheral surface 21 of theinner ring 20C, and the contact area is zero. That is, thelip part 33 is in an opened state. Also, like an example ofFIG. 11 , a configuration is also possible in which when the compressed air is applied, the inner peripheral surface of the radially inner periphery end of thelip part 33 and the outerperipheral surface 21 of theinner ring 20C are in contact with each other and the contact area between the innerperipheral surface 35 of thelip part 33 and the outerperipheral surface 21 of theinner ring 20C is reduced, as compared to when the compressed air is not applied. - Particularly, in the sixth embodiment, since the
seal member 30E is configured only by the elastic material without a metal core, the seal member is likely to be elastically deformed, as a whole. For this reason, when the compressed air exceeding a specific pressure is applied to theseal member 30E, the inner peripheral part of theseal member 30E is elastically deformed outward in the axial direction, and the contact area between the inner peripheral surface of thelip part 33 and theinclined surface 23 of theinner ring 20 is reduced. - In the meantime, when the supply of the compressed air is stopped so as to stop the air turbine handpiece for dental use, the compressed air is not applied to the
lip part 33, so that thelip part 33 returns to the state as shown inFIG. 8 . The inner peripheral surface of thelip part 33 is surface-contacted to the outerperipheral surface 21 of theinner ring 20C with generating the pressing force. That is, thelip part 33 is in a closed state. Thereby, thelip part 33 functions as a brake of theinner ring 20C and the rotary shaft 101 (refer toFIG. 1 ), to which theinner ring 20C is fixed, so that it is possible to promptly stop therotary shaft 101. - Also, the
lip part 33 is formed to have an inclined shape that is inclined to the downstream side with respect to the supply direction of the compressed air toward the radially inner side and can be thus easily elastically deformed by the compressed air. Therefore, it is possible to perform the operation of opening and closing thelip part 33 by the compressed air with good sensitivity. - In the meantime, as shown in
FIG. 9 , the inclination angle θ of thelip part 33 of theseal member 30E is preferably set to 35° to 55°. Thereby, when the compressed air is applied, the air is efficiently applied to thelip part 33, so that it is possible to smoothly open theseal member 30E. As a result, it is possible to implement the rotation at ultrahigh speed with the low pressure of the compressed air. - Also, since at least the part, to which the
lip part 33 is contacted, of the outerperipheral surface 21 of theinner ring 20C is configured as the cylindrical surface, it is possible to increase the contact area between the outerperipheral surface 21 of theinner ring 20C and the inner peripheral surface of thelip part 33, thereby improving the brake function of thelip part 33. Particularly, in the sixth embodiment, since the inner peripheral surface of thelip part 33 is surface-contacted to the cylindrical outerperipheral surface 21 of theinner ring 20C, it is possible to further improve the brake function of thelip part 33. - In the meantime, the radially inner peripheral surface of the
lip part 33 may have a substantially triangular section. In this case, as compared to the above surface-contact configuration, the brake performance is lowered. However, when the compressed air is applied, it is possible to open theseal member 30E with the slight elastic deformation. Accordingly, it is possible to implement the rotation at ultrahigh speed with the low pressure of the compressed air. - Subsequently, a seventh embodiment of the
bearing unit 100 for an air turbine is described. -
FIG. 12 is a partial sectional view depicting a rolling bearing of a seventh embodiment. - As shown in
FIG. 12 , aninner ring 20D of a rollingbearing 1F may more extend outward in the axial direction than theouter ring 10 and aseal member 30F may more extend outward in the axial direction than theouter ring 10, inasmuch as the seal performance is obtained. In this case, the inner peripheral surface of thelip part 33 of theseal member 30F is in contact with the outerperipheral surface 21 of theinner ring 20D at the more axially outer side than theouter ring 10. According to this configuration, since it is possible to largely incline thelip part 33, it is possible to more easily perform the operation of opening and closing thelip part 33 by the compressed air. - The present invention is not limited to the above embodiments, and can be appropriately modified and improved.
- The
cage 5 that is used for the rollingbearing 1 of the first to seventh embodiments is configured so that therim part 7 provided at one end-side thereof is arranged at the more upstream side with respect to the supply direction of the compressed air than theball 3. However, the present invention is not limited thereto. For example, therim part 7 may be arranged at the seal member-side of the axially opposite side. - Also, since the seal member is arranged only at one axial end-side of the rolling
bearing 1, thegroove portion 13 of theouter ring 10, theinclined surface 23 of theinner rings step surface 67 are formed only at one axial end-side. However, the present invention is not limited thereto. For example, they may also be symmetrically formed at the other axial end-side. In this case, one of a pair ofgroove portions 13 is not used, and in the configurations of the first to fifth embodiments, a pair of inclined surfaces or steps is not used. In this case, in a process of assembling the rolling bearing, it is not necessary to consider a mounting direction, so that it is possible to simplify the operation process. - Also, the lip part of the seal member may have a thickness that is constant or gradually decreases toward the radially inner side.
- Also, a shape of the inner diameter-side end portion of the
lip part 33 of the seal member may be substantially elliptical or triangular, as shown inFIGS. 13 and14 . The other examples of theseal member 30 to be described below can also be applied to theseal members - Also, the inner diameter-side end portion of the
lip part 33 may be provided with at least oneventilation hole 41, as shown inFIG. 15 , or may be provided with at least one slit 43, as shown inFIGS. 16 to 18 . Meanwhile, inFIG. 15 , the example where onecircular ventilation hole 41 is provided is shown. However, the two or more ventilation holes 41 may be provided, and the shape of theventilation hole 41 is not limited to the circular shape. Also,FIGS. 16 to 18 show the examples where the twoslits 43, the fourslits 43 and the eightslits 43 are respectively provided with being equidistantly spaced in a circumferential direction. However, the numbers and circumferential intervals of theslits 43 are not limited thereto. - Also, as shown in
FIGS. 19 to 21 , the inner diameter-side end portion of thelip part 33 may be notched continuously in the circumferential direction and the inner diameter-side end portion of thelip part 33 may be in partial contact with the outerperipheral surface 21 of theinner ring 20. - Here, the
seal member 30E of the sixth embodiment is exemplified.FIG. 22A is a sectional view taken along a line A-A ofFIGS. 19 to 21 , andFIG. 22B is a sectional view taken along a line B-B ofFIGS. 19 to 21 . - Like this, the present invention is not limited to the above embodiments, and combinations of the respective configurations of the embodiments and changes and applications made by one skilled in the art on the basis of the specification and the well-known technology are also included within the scope of the present invention.
- For example, in the embodiments, the ball bearing is used as the rolling bearing. However, the other rolling bearing such as a roller bearing can also be used. Also, in the embodiments, the rolling bearing is an inner ring rotation type and the seal member is fixed to the outer ring. However, a configuration where the seal member is fixed to the inner ring and is in contact with the outer ring is also possible. Also, a configuration is possible in which the shape of the cage is changed to increase the bearing width, as compared to the above embodiments.
- Also, the rolling bearing of the present invention may be an angular-type rolling bearing.
-
FIG. 23 is a partial sectional view of an angular-type rolling bearing having acounterbore 81 formed in anouter ring 10A. Theinclined surface 23 and theseal member 30 of the rollingbearing 1 of the first embodiment are applied to theouter ring 10A and theinner ring 20, for example. -
FIG. 24 is a partial sectional view of an angular-type rolling bearing having acounterbore 83 formed in an inner ring. Also in this case, theinclined surface 23 and theseal member 30 of the rollingbearing 1 of the first embodiment are applied to theouter ring 10 and theinner ring 20E. - As shown in
FIGS. 23 and 24 , even with the angular-type rolling bearing, the similar operational effects to the above-described operational effects are accomplished. Meanwhile,FIGS. 23 and 24 just show the examples, and the rolling bearings 1A to 1F of the other embodiments can be configured by the above angular-type rolling bearing or by another angular-type rolling bearing. - The subject application is based on Japanese Patent Application Nos.
2016-43309 filed on March 7, 2016 2016-100601 filed on May 19, 2016 2016-129149 filed on June 29, 2016 -
- 1, 1B, 1C, 1D, 1E, 1F: rolling bearing
- 3: ball (rolling element)
- 5: cage
- 7: rim part
- 10, 10A: outer ring
- 11: inner peripheral surface
- 13: groove portion
- 15: tapered surface
- 17: axially inner surface
- 20, 20A, 20B, 20C, 20D, 20E: inner ring
- 21: outer peripheral surface
- 23: inclined surface
- 30, 30A, 30C, 30D, 30E, 30F: seal member
- 31: base part
- 33: lip part
- 35: inner peripheral surface
- 40: snap ring
- 41: ventilation hole
- 43: slit
- 67: step surface
- 100: bearing unit for an air turbine
- 200: air turbine handpiece for dental use
- 201: head part
- S: bearing internal space
Claims (4)
- A bearing unit for an air turbine comprising:a turbine blade configured to rotate with receiving compressed air;a rotary shaft having the turbine blade integrally fixed thereto and capable of mounting a tool thereto; anda rolling bearing configured to rotatably support the rotary shaft to a housing,wherein the rolling bearing comprises:an outer ring fixed to the housing;an inner ring fixed to the rotary shaft;a plurality of rolling elements rollably arranged between the outer ring and the inner ring; anda seal member fixed to an inner peripheral surface of the outer ring and configured to seal a bearing internal space between the outer ring and the inner ring,wherein an axial end, which is positioned at a downstream side with respect to a supply direction of the compressed air, of an outer peripheral surface of the inner ring has an inclined surface having a diameter that changes from large to small toward the downstream side with respect to the supply direction of axial compressed air,
wherein the seal member is configured only by an elastic material without a metal core, and has a base part extending in a radial direction and a lip part extending from a radially inner end of the base part and inclined to the downstream side with respect to the supply direction of the compressed air toward a radially inner side,
wherein when the compressed air is not applied, an inclined surface, which is positioned at an upstream side with respect to the supply direction of the compressed air, of the lip part of the seal member is in contact with the inclined surface of the inner ring, and
wherein when the compressed air is applied, a contact area between the inclined surface, which is positioned at the upstream side with respect to the supply direction of the compressed air, of the lip part of the seal member and the inclined surface of the inner ring becomes smaller, as compared to when the compressed air is not applied. - A bearing unit for an air turbine comprising:a turbine blade configured to rotate with receiving compressed air;a rotary shaft having the turbine blade integrally fixed thereto and capable of mounting a tool thereto; anda rolling bearing configured to rotatably support the rotary shaft to a housing,wherein the rolling bearing comprises:an outer ring fixed to the housing;an inner ring fixed to the rotary shaft;a plurality of rolling elements rollably arranged between the outer ring and the inner ring; anda seal member fixed to an inner peripheral surface of the outer ring and configured to seal a bearing internal space between the outer ring and the inner ring,wherein at least a part, with which a lip part is in contact, of an outer peripheral surface of the inner ring is configured as a cylindrical surface,
wherein the seal member is configured only by an elastic material without a metal core, and has a base part extending in a radial direction and the lip part extending from a radially inner end of the base part and inclined to a downstream side with respect to a supply direction of the compressed air toward a radially inner side,
wherein when the compressed air is not applied, an inner peripheral surface of the lip part of the seal member is in contact with the cylindrical surface of the inner ring, and
wherein when the compressed air is applied, a contact area between the inner peripheral surface of the lip part of the seal member and the cylindrical surface of the inner ring becomes smaller, as compared to when the compressed air is not applied. - The bearing unit for an air turbine according to claim 1 or 2,
wherein when the compressed air is applied, the seal member is not in contact with the outer peripheral surface of the inner ring. - An air turbine handpiece for dental use comprising the bearing unit for an air turbine according to one of claims I to 3.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP19219903.2A EP3667110B1 (en) | 2016-03-07 | 2017-03-07 | Rolling bearing for a roller bearing unit for air turbine and air turbine handpiece for dental use |
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2016043309A JP6651912B2 (en) | 2016-03-07 | 2016-03-07 | Rolling bearings and bearing units for air turbines |
JP2016129149A JP6686738B2 (en) | 2016-05-19 | 2016-06-29 | Rolling bearings and bearing units for air turbines |
PCT/JP2017/009102 WO2017154935A1 (en) | 2016-03-07 | 2017-03-07 | Rolling bearing, bearing unit for air turbine, and air turbine handpiece for dental use |
Related Child Applications (2)
Application Number | Title | Priority Date | Filing Date |
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EP19219903.2A Division-Into EP3667110B1 (en) | 2016-03-07 | 2017-03-07 | Rolling bearing for a roller bearing unit for air turbine and air turbine handpiece for dental use |
EP19219903.2A Division EP3667110B1 (en) | 2016-03-07 | 2017-03-07 | Rolling bearing for a roller bearing unit for air turbine and air turbine handpiece for dental use |
Publications (3)
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EP3428468A1 true EP3428468A1 (en) | 2019-01-16 |
EP3428468A4 EP3428468A4 (en) | 2019-01-16 |
EP3428468B1 EP3428468B1 (en) | 2020-04-22 |
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EP17763275.9A Active EP3428468B1 (en) | 2016-03-07 | 2017-03-07 | Rolling bearing, bearing unit for air turbine, and air turbine handpiece for dental use |
EP19219903.2A Active EP3667110B1 (en) | 2016-03-07 | 2017-03-07 | Rolling bearing for a roller bearing unit for air turbine and air turbine handpiece for dental use |
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EP19219903.2A Active EP3667110B1 (en) | 2016-03-07 | 2017-03-07 | Rolling bearing for a roller bearing unit for air turbine and air turbine handpiece for dental use |
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EP (2) | EP3428468B1 (en) |
CN (2) | CN111503161B (en) |
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CN114867948A (en) * | 2019-12-27 | 2022-08-05 | 日本精工株式会社 | Rolling bearing for air turbine |
CN114901960A (en) * | 2019-12-27 | 2022-08-12 | 日本精工株式会社 | Rolling bearing for air turbine |
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KR102019991B1 (en) * | 2018-11-23 | 2019-09-09 | 엘지전자 주식회사 | Motor |
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- 2017-03-07 CN CN201911379644.5A patent/CN111503161B/en active Active
- 2017-03-07 CN CN201780016093.9A patent/CN108713108A/en active Pending
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CN114867948A (en) * | 2019-12-27 | 2022-08-05 | 日本精工株式会社 | Rolling bearing for air turbine |
CN114901960A (en) * | 2019-12-27 | 2022-08-12 | 日本精工株式会社 | Rolling bearing for air turbine |
EP4083453A4 (en) * | 2019-12-27 | 2023-01-18 | NSK Ltd. | Rolling bearing for air turbine |
EP4083454A4 (en) * | 2019-12-27 | 2023-02-08 | NSK Ltd. | Rolling bearing for air turbine |
US11953057B2 (en) | 2019-12-27 | 2024-04-09 | Nsk Ltd. | Rolling bearing for air turbine |
US11965557B2 (en) | 2019-12-27 | 2024-04-23 | Nsk Ltd. | Rolling bearing for air turbine |
EP4119808A4 (en) * | 2020-03-12 | 2023-08-02 | NSK Ltd. | Rolling bearing |
Also Published As
Publication number | Publication date |
---|---|
WO2017154935A1 (en) | 2017-09-14 |
CN108713108A (en) | 2018-10-26 |
EP3428468B1 (en) | 2020-04-22 |
EP3667110A1 (en) | 2020-06-17 |
CN111503161B (en) | 2022-06-21 |
CN111503161A (en) | 2020-08-07 |
EP3667110B1 (en) | 2021-07-07 |
EP3428468A4 (en) | 2019-01-16 |
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